Supercharger pump or motor



Feb. 5, 1946,

J. F. JAWOROWSKI ETAL.

SUPERCHARGER PUMP OR MOTOR 9 Sheets-Sheet l 'Filed Feb. 21, 1941 Feb. 5, 1946. J, F, JAwoRowsKl ET AL 2,394,185

SUPERCHARGER PUMP OR MOTOR 9 Shees-Sheet 2 f #wail ATTQBNEYS Feb. 5, 1946. J. F. JAwoRowsKl ETAL, 2,394,185

- SUPERCHARGER PUMP 0R MOTOR Filed Feb. 21, 1941 9 sheets-Sheet :s

Feb. 5, 1946. J. F. J'AwoRowsKl x-:TAL 2,394,185

SUPERGHARGER PUMP 0R Mo'ronv Filed Feb. 21, 1941 9 Sheets-sheet 4 '46e Y @M INV ENTOR. JOSEPH F? 7A WOFOWSK/ ATE/VEYS V73 .ZO 7; g BY Feb. 5, 1946. J. F. JAwoRowsKl ETAL 2,394,185 I SUPERCHARGER PUMP 0R MOTOR Filed Feb. 2l, 1.941 9 Sheets-Sheet 5 INVENTORS JOSEPH l? 7,4 www ws/ /VOEEEET `AwoiPows-,v/

BY wvl/WM v Feb. 5, 1946. J. F. JAwoRousKl ETAI. 2,394,185

SUPERCHARGER PUMP 0R MOTOR Filed Feb. 2l, 1941 9 sheets-Shen e II l' l. I/I

I AroP/VEVS Feb.. 5, 1946 J. F. JAwoRowsKl ETAL 2,394,185

SUPEBCHARGEI; PUMP 0R Mo'ron Filed Feb. 21, 1941 9 sheets-sheet 7 www@ ATTORNEYS 9 sheets-sheet 8 INVENTOR. Jos-PH 77m wozeowsk/ Noam-25T fAworowsA/l ATTORNEYS J. F. .JAwoRowsKl ETAL SYUPERCHARGER PUMP 0R MOTOR Filed Feb. 21, 1941 Feb. 5, 1946.

Feb. 5, 1946. J. FfJAwoRowsKl ETAI..

SUPERCHARGER PUMP 0R MOTOR Filed Feb. 21, 1941l 9 sheets-snede A r rp PA/frs Patented Feb. 5, i945 2,394,185 snrEacnAnGEn PUMP on Moron 4.inseriti r.

Jaworows Cleveland Heights, and Norbert J aworowski,

Cleveland, Ohio pplication lFebruary 21, 1941, Serial No. 379,930

16 Claims.

This invention relates to apparatus of the rotary engine type which is adapted for use either as a iiuid pump or a fluid pressure motor. More particularly our invention relates to improvements in vane type rotary machines which may be employed for delivering a substantially nonpulsating, constant gaseous, under the desired conditions of pressure and volume, or may be used as a pressure driven motor.

One of the most important uses of our rotary machine is for super-charging aircraft cabins and engines but it is also equally suitable for supplying air or other gas under pressure for other purposes, for pumping liquids, or for use as a motor. In this specification and in the drawings a cabin supercharger is described but it will bc understood that liquid pumpsand iiuid pressure actuated motors also come within the scope of our invention and the description and drawings herein are intended to be illustrative rather than limiting in eect.

In fluid pumping apparatus it is usually desirable to supply the output of the pump at a substantially constant, non-fluctuating or nonpulsating pressure. Centrifugal pumps and -superchargers of various types have been used to accomplish this general purpose but, particularly for aircraft supercharger work., such centrifugal devices must operate at extremely high speeds and are relatively bulky and inefficient due to the unavoidable slippage losses inherent in centrifugal pumps.

It is among the objects of our present invention to provide a compact, emcient, lightweight rotary pump, blower or motor which, when used as a pump or blower, will supply a substantially constant pressure output and which will occupy a minimum of space for its pumping capacity,

and which, when used yas a motor, will effectively convert fluid pressure into rotary movement.

Other objects of our invention are: the provision of a uid pump or motor of the rotating vane type having a minimum of moving parts and which is simple and compact in construction and susceptible to economical manufacture; the provisioncf a rotating vane type pump adapted to deliver a continuous and substantially non-liuctuating discharge of fluid at all points in the rotation of the impeller blade or vane; the proiiow of iiuid, either liquid or lll vision of a rotary machine of the type described in which wear and friction of the moving parts is reduced to a minimum and which may therefore be made largely of lightweight materials such as aluminum or its alloys;

particularly adapted for supercharger uses, which may be operated at relatively low speeds while delivering the desired volume of iuid at the desired pressure; the provision of a vane type pump which will deliver fluid continuously and which may be run for long periods` of time with the pumping parts unlubricated and which may therefore be used successfully for heavy duty work where relatively high temperatures are encountered; the provision of a continuous delivery, positive displacement supercharger in which means are provided for eectively preventing the entry 0i lubricant from the bearings into the uid discharged from the pump; the provision of a pump or supercharger which will deliver a maximum output with a minimum of power; and the pro vision of a very compact, rugged and emcient uid pressure actuated motor.

The above and other .objects of our invention will appear from the following description of one embodiment thereof, particularly designed and intended for use as an airplane cabin. supercharger, reference being had to the accompanying drawings, in which- Figure 1 is a vertical cross-sectional assembly view of a structure embodying our invention in the form of a uid pump,` the vane being in the position shown in Figure 3 and the section being taken substantially on line l-i of Figure 3.

Figure 2 is a transverse cross-sectional view of our pump taken substantially on line 2 2 of Figure 1, but illustrating the vane in a position 90 removed from that shown in Figure l.

Figure 3 is a transverse cross-sectional view through our machine, similar to Figure 2 except that the vane has moved 90 in pumping direction into the same position as shown in Figure 1.

Figure 4 is a view similar to Figures 2 and 3 but illustrating the vane advanced 90 from Figure 3. Figure 5 is a view similar to Figures-2, 3 and 4, but illustrating the vane in its top position, advanced 90 from Figure i.

Figure 6 is a transverse cross-sectional view 5 through our pump structure taken on line 6-6 the provision of a positive displacement fluid pump,

of Figure 1 but illustrating the vane in the same position as in Figure 2 and showing the inlet passages through the vane.

Figure 7 is a detached side elevation of the anti-friction or wear plate for the inlet side of the vane.

Figure 8 is a cross-sectional view taken on line 88 of Figure 7.

Figure 9 is a detached side elevation of the wear plate for the discharge side ci' the vane.

Figure 10 is a cross-sectional view taken on line I-I l) of Figure 9.

Figure 11 is a transverse cross-sectional view through the supercharger structure taken on line li-II oi' Figure 1 and illustrating the air inlet passages to the pumping chambers.

Figure 12 is a detached vertical cross-sectional view of the discharge end housing.

Figure 13 is a detachedV vertical cross-sectional view of the discharge end outer sleeve support.

Figure 14 is a detached vertical cross-sectional view of the discharge end inner sleeve and shaft support. Figures 12, 13 and 14 are all aligned to illustrate the various axes or center lines of the parts.

Figure 15 is a transverse cross-sectional view taken on line I--l 5 of Figure 14.

Figure 16 is a detached vertical cross-sectional sub-assembly view through the vane and shaft assembly.

Figure 17 is a vertical cross-sectional view of the drive portion of the vane shaft.

Figure 18 is an end elevation of the member shown in Figure 17.

Figure 19 is a vertical cross-sectional view taken on line I9-i9 of Figure 17.

Figure 20 is a vertical cross-sectional view taken on line 2li-20 of Figure 1'1.l

Figure 21 is a detached side elevation taken from the discharge side of the vane, the wear plates being removed. v

Figure 22 is an end elevation of the vane shown in Figure 21.

Figure 23 is a transverse cross-sectional view through one of the discharge ports of the vane takenv on line 23-23 of Figure 21.

Figure 24 is a side elevational view, similar to Figure 21, but taken from the opposite or inlet side of the vane.

Figure 25 is a transverse cross-sectional view taken on line 25-25 of Figure 24 and illustrating the inlet passages through the vane.

Figure 26 is a fragmentary longitudinal vertical cross-sectional view of the vane taken on line 26-26 of Figure 22.

Figure 27 is a horizontal cross-sectional view of the vane taken on line 21-21 of Figure 21.

Figure 28 is a fragmentary view of the corner of the vane, generally similar to Figure 26, but showing the end bearing or wear plate in position.

Figure 29 is a detached perspective view of one of the end wear plates for the vane.

Figure 30 is an enlarged vertical cross-sectional view through one of the attaching buttons for the end wear plates.

Figure 31 is a detached elevational view of the inner rotatable sleeve.

Figure 32 is a fragmentary cross-sectional view taken on line 32-32 of Figure 31 and showing the formation of the slot in the sleeve through which the vane extends.

Figure 33 is a detached elevational view of one of the sealing bars which are inserted in the edges of the slots in the rotatable sleeves.

asoman Figure 34 is an enlarged cross-sectional view taken on line '34-34 of Figure 33.

Figure 35 is a fragmentary enlarged cross-sectional view taken on line 35--35 of Figure 31 and illustrating the sealing bars in position in the grooves in the edges of the vane slot.

In modern high altitude airplane operation it is very desirable to provide means for maintaining the pressure conditions within the cabin equal to the conditions which exist at relatively low altitudes. This is important in order to supply the pilot, crew .and passengers of the aircraft with a proper amount of oxygen and to avoid the necessity. for wearing individual oxygen masks. The supercharging of aircraft engines is also necessary in order to maintain their power output at high altitudes and our invention is equally adaptablel for maintaining the pressure in a sealed cabin at the desired low altitude value and=for supplying air to the engines at low altitude pressures.

Various types of vane type pumps or blowers have been proposed and used, one successful form of which is illustrated and described in U. S. Letters Patent No. 1,989,864 to J. F. Jaworowski. In this type of pump a vane rotates concentrically within a stationary cylindrical casing and a tubular cylindrical sleeve is rotatably mounted eccentricaliy within said casing, the vane protruding through a slot in thesleeve. This type of pump produces a pulsating or uctuating output due to the fact that the discharge pressure of the pump drops to zero during a portion of each revolution of the vane. Furthermore, the apparatus of this patent cannot be used as a motor because it will not continue to rotate when pressure is applied. In our present invention these difllculties have been overcome and the discharge is continuous and at substantially constant pressure through- Furthermore, a continuous pressure is applied against the vane when our apparatus is used as a motor.

Referring to Figure 1 of the drawings, the cylindrical casing I of the cabin supercharger illustrated denes the outside of the pumping chamber of the unit and is preferably provided with cooling ns 2 and disposed between the discharge end housing 3 and the drive end housing 4. These housings 3 and 4 with their associated parts form closuresfor the ends of cylinder I and are secured thereto by suitable screws 5, a dowel pin 6 being provided tc facilitate assembly.

The drive shaft is generally indicated at S and is supported concentrically with the cylindrical bore of the cylinder i in bearings housed within the end casings 3 and 4. Carried by and rotatable with the shaft S is the blade or vane V which has its outer periphery formed on the 00 same curvature as the cylinder l and which rotates within the cylinder i with just sufficient clearance to. avoid undue wear while maintaining the seal necessary for eicient operation.

Eccentrically and rotatably supported within the end housings 3 and 4 is a large outer cylindrical sleeve l having its center of rotation above the common center line of the shaft S and cylinder i (see Fig. 1). Also eccentrically and rotatably supported Within the end housings 3 and 4 is a small inner cylindrical sleeve 8 which rotates on a center line disposed below the center line of the shaft S and housing I.

In Figure 2 `the center line of the stationary cylinder is indicated at 'a, the center line of the large outer rotatable sleeve at b and the center out the entire revolution of the blade or vane.

plane, the centers of rotation of the inner and outer sleeves being disposed on opposite sides of and in alignment with the center or longitudinal axis of the stationary cylinder I.

28 of the lvane being preferably serrated or As is clearly seen in Figures 2to 6, the outer sleeve 1 is tangent to the stationary cylinder l at what may be termed theftop of the pump structure. Of course, the entire pump as a unit might be disposed in any angular position but, for

`purposes of the present description, the portion of the apparatus where the cylinder I and sleeve 1 are tangent will be referred to as the upper or top portion. The outer surface of the small sleeve`8 is tangent to the inner surface of the large sleeve 1 at a point diametrically opposite from the point of tangency between cylinder I and large sleeve 1. At these points of tangency a close running fit is maintained as there is relative movement between the parts during operation of the pump.

The supporting means for the large sleeve 1, small sleeve 8, and shaft S together with the rotatable vane V, will now be described.

As the parts at each end of the pump structure are substantially identical only those members which are disposed at the discharge end of the pump (the left hand end as seen in Figure 1) will be' described in detail, and it will be understood that the corresponding parts which are located at the drive end' of the pump (the right hand end, as seen in Figure 1) will be substantially the same except that they are of opposite hand. Similar reference characters have in most instances been applied to similar parts atv each end of the unit. The large sleeve 1 is rotatably supported on an anti-friction bearing 9 mounted on the outer sleeve supporting member indicated generally at I8 and seen in detail in Figure 13. The end housing 3 (seen in detail in Figure 12) has a flange II on its end wall which defines a recess' concentric with the longitudinal axis b of thev outer sleeve 'I. The support member I0 seats in this recess and the bearing 9 is concentric with the center of the recess formed by the flange II and thus the sleeve 1 is 'supported tangent to the cylinder I.

The inner sleeve and shaft supporting member for the discharge end is indicated generally at I2 and-is seen in detached cross-sectionalview in Figure 14. This member includes a tubular outlet conduit portion I3 which extends through a bore I4 in the outer sleeve support I8. A nut I5 is threaded on to the end of the sleeve I3 and an anti-friction bearing I6 is carried by the support I2. When the nut I5 is tightened the bearing I6 is urged against the base of the recess 'I1 in the outer sleeve support III. Screws Iahold the outer sleeve support I8 firmly against the end of housing 3 in the recess formed by flange II.

The tubular portion port forms the discharge outlet for the pump, as will appear later. The center line of this tubular portion I3 lies upon the longitudinal axis of the pump cylinder I and a bearing I8 is supported concentricallywith the axis of cylinder I within the cup shaped inner end portion I9 of support member I2. The shaft S is mounted in the bearing I8 and thus rotates on the center line of. the cylinder I.

As the vane V is carried by the shaft S it will be observed that rotation of the shaft sweeps the Vane around the cylinder I, the outer edge I3 of the inner sleeve supgrooved at 28' and shaped to provide a close sliding fit with the inner surface of the cylinder I.

vWhen power is applied to the projecting end 2l of the shaft S to rotate sanie in the direction of the arrow (Figs. 1 and 2) the vane V will rotate within the cylinder I with its outer edge 20 engaging the inner surface of the cylinder and with its end surfaces engaging the faces which form the ends of the cylinder. At the outlet end of the pump these faces include the surface 22 on the outer sleeve support I0, the surface '23.on the end housing 3. and the ends of the slots in the outer and inner sleeves 1 and 8. Similar end faces define the oppositel end of cylinder I. This rotation of the vane V will rotate the outer sleeve 1 and inner sleeve 8 about their respective axes, the outer sleeve 1 remaining at all times tangent to the cylinder I' and the inner sleeve 8 remaining at all times tangent to the inner surface of the outer sleeve 1 at a point diametrically opposite the point of tangency of the outer sleeve 'I with the stationary cylinder I.

The only moving parts in ourpump structure are the shaft-vane assembly which rotates aboutl the center a of the s ationary cylinder I, the large or outer sleeve which rotates about its center b above the center a, and the small or in'- ner sleeve which 5rotates about the center c belowl the center a.

The shaft and portion 24, a tubular outlet shaft portion 32, and the vane V. The member 24 is mounted in the anti-friction bearing I8 at the drive end of the machine and its end 2I extends out through the end casing '4 and is connected by any suitable means to any suitable source of'power (not shown).y The enlarged vane supporting portion 25 of the shaft section 24 is slotted at V26 to permit the vane to be inserted therein. This slot 26 is not continuous throughout its length but is closed at its top throughout a portion intermediate its ends by the web 21. vFurthermore, the slot 26 does not extend to the ends of portion 25 butYY connects to bores 28 which, as is clearly seen in Figure 1'1, extend almost to the reduced shaft portion 24. A series of fluid passages 29 extend through the sides of the vane carrying portion 25 into the slot 26 and when the vane is, assembled with the shaft these holes line up with corresponding holes in the vane, which will be later described. At the left hand end of the shaft section 24 (Fig. 1'1) a circular recess 38 is formed and a radially extending groove 3l projects outwardly from this recess.

The discharge portion of the shaft S comprises a generally tubular member 32 which fits within the bore 28 in the drive portion 24 of the shaft. A iiange 33 on the tubular shaft section 32 is disposed in the recess .30v and a lug 34 extends radially outwardly from the flange 33 and lies within the groove 3I in the driving portion of. the shaft whereby-relative angular displacement between the parts 24 and 32 of the shaft is prevented. The inner end of tubular shaft portion 32 stops just short of the bottom of the bore 28. A fluid' discharge passage 35 is formed by vthe interior of the shaft member 32 and a relatively small hole 36 extends through the closed end 31 of the tubular shaft member. The shaft drive section 24 is preferably formed with a hole 38 extending in from its end 2| to the bore 28. This hole is normally closed by a screw plug 39 and is lprovided so that, vwhen it is desired blade assembly is illustrated in Figures 16 to 29 'and includes the drive end shaft to aisassembie the paris, a roe may be inserted through the hole 38 to engage the end of the tubular member 32 andrdrive it out of its fitwithin the -bore 28.

The vane V is illustrated in detail in Figures 21 to 29. It comprises essentially a fiat sidedgenorally rectangular body having upwardly projecting spaced lugs 40 and 4| at its top. The width of the blade is such as to provide a close t within the slot in the drive shaft portion 25 and the lugs 40 and 4| extend upinto the apertures 42 and 43. The outer surfaces of the lugs 48 and 4| are curvedto correspond to the radius -of the anges 44 and 45 at the ends of slot 26 of the vane carrying section of the shaft. A

longitudinal bore 46 extends through the body of the vane and when the vane is assembled with the shaft parts the tubular discharge section 82 extends through this bore 46.

Referring to -Figure 16, it will be seen that by the above described structure a rugged and simple shaft and vane assemblyvis provided, the shaft parts 24 and 32 being flrst separated, the vane then being inserted into the slot 26 with the lugs 40 and 4| extending up into the apertures 42 and 43. The tubular shaft 32 is then inserted into the bore 28 and through bore 46 of the vane until the flange 33 seats in the groove 30 and the lug 34 is located in the slot 3|. After the shaft and vane parts are assembled' and installed in the pump structure longitudinal displacement of the shaft sections and vane is prevented by the supporting bearings I8 and I8 which are rigidly held in position in the end housings 3 and 4.

For manufacturing reasons holes 41 extend through the lugs 48 and 4| to the bore 46. For

the same reason holes 48 extend through the top `tions -2 to reduce fluid flow resistance, to holes 53 which extend from the fluid receiving passages into the bore 46.

On the opposite section or trailing side of the vane (see Fig. 24) inlet apertures 54 are disposed in staggered arrangement to the discharge apertures 50 on the leading side of the vane. Apertures 54 connect with passages 55 in the body of the vane, which passages extend upwardly to a point just short of the bore 46 and terminate in passages 56 and 51 which extend upwardly and outwardly to the face of the vane. The lower portions of the apertures 55 are also preferably curved as seen at 58 to reduce resistance to the passage of fluid therethrough.

In order to reduce wear and friction between a series of spaced holes 60 which define the fluid passages into the interior chambers 55 in the vane. The side of the vane is recessed at 6| and longitudinally extending grooves 62 and 63 are formed at the top and bottom of this recess.r 'I'he edges of plate 59 are formed to t in the grooves 62 and 63, as seen at 64 and 65, and, in assembling the vane, the plate 59 is slid into position from one end. When the side plate is in position the side face of the vane is generally flat, except for curved depressions referred to below and indicated in dot and dash lines in Figure 22, and the holes 60 are lined up with the openings 54 in the vane body. In like manner the side plate 66 slides into the' grooves 61 and 68 on the leading side of the vane. Slotted holes 69 in the plate 66 align with the holes 50 in the vane body and form the passages through which' the fluid being pumped enters the chambers 5| in the vane.

The wear plates 59 and 66 are formed with shallow concave depressions 10 and 1| in their upper portions above the slotted holes 60 and 69 respectively. These concave depressions are provided to permit the necessary change in the angular relation between the edges of the slot in the innersleeve 8 and the side faces of the vane V while maintaining substantial engagement at all times between the faces of the vane and the edges of the slot. In like manner, shallow concave depressions 12 and 13 are formed on the outer surfaces of the plates 59 and 66 below the depressions 18 and 1|. These lower concave grooves extendl longitudinally of the wear plates and are formed on a longer radius than the depressions 10 and 1I in order to permit the necessary tilting action between the edges of the slot in the large sleeve 1 and the opposite faces of the vane during rotation thereof.

Referringto Figures 2 to 5 inclusive it will be observed that as the vane rotates lines joining the points of contact between the edges of the slots in the sleeves 1 and 8 and the vane shift or tilt. In Figures 3 and 5 these lines are horizontal while in Figures 2 and 4 they are angularly disposed and the provision of the shallow concave recesses 18, 1|, 12 and 13 in the blade faces permits this tilting to take place without binding and while substantially maintaining contact between both the leading and trailing faces of the vane and the respective edges of the slots in the outer and inner sleeves 1 and 8.

In order to retain the side wear plates 59 and l 66 in position and to provide suitable bearing surfaces for the ends of the vane where they engage the surfaces 22 and 23, we employ removable end wear plates, one of which is seen in perspective view in Figure 29. These plates are flat on their outer surfaces, have their edges contoured to align with' the recessesl 10, 1|, 12 and 13 in the side plates, and have projecting ribs 15 on their inner surfaces. Holes 16 and 11 extend through the end plates and are counter boredon their outer surface, as seen at 18 (Fig. 28). Attaching buttons 19 extend through the holes 16 and 11 with their enlarged h'ead portions 80 disposed in the counter bores 18. An annular groove 8| is formed in the inwardly extending shank of the buttons 19. To attach' the end wear plate 14 in position the buttons are inserted into the holes 16 and 11 and their rounded inner heads 82 thrust through the upper portions 83 of keyhole shaped openingsin the ends of the vane. These openings are seen in Figures 22, 26 and 28 and it will also be observed from Figures 22 and 26 that a charge chambers or passages trailing edge.

end 91 of the slot in shaft member 25, thus peredge 91 of the slot 90, is intended primarily to reduce wear, it seats against the bottom of the slot 92 and remains seated during operation of the supercharger. On the leading edge 99 of the slot v99 the sealing bar 93 is similarly disposed but holes 99 extend from the outer surface of the sleeve 8 into the base of the slot 9|. As pressure is generated during operation of the pump against the leading face of the vane this pressure will be transmitted through the Aholes 99 against the chamfered face |99 of the bar 93 dismitting the vane to center itself in the cylinder When th'e end wear plates 14 are attached on the opposite ends of the vane they lock the sidewear plates 59 and 86 in position as they overlap the ends of the side plates. After the entire shaft' and vane assembly is completed the end plates 'it are locked in position by the flanges 44 and B5 v of the sh'aft and thus a, structure is provided which, although quickly and easily assembled, cannot become dissembled when in working position. ItV will be understood that each of the two .end plates 14 is secured in position in exactly the same manner, and although reference has been made largely to one end of th'e vane, the same arrangement is provided at the opposite end.

Having described in detail the vane and the openings and passages therein reference is now made to Figure 16 showing the assembly of the vane and shaft. It will be seen that the dis- !il and the h'oles 53 are aligned with and connected to argularly disposed holes 89 which extend through the wall of the shaft 32 into the discharge passage 3d. The iiuid inlet openings and chambers 59 and b5 are connected through their adjoining holes 59 and 5l to the holes 29 which exterd th'rough the enlarged central portion 2t `of the shaft structure. Thus, it will be seen that the openings 99 in the inlet side wear plate '59 are connected through the blade and shaft into the space A within the inner sleeve 9 (see Fig. 6), andthe slotted openings t9 in the discharge face wear plate 69 are connected to the interior of the hollow shaft 32 (see Fig. 2).

The outlet end of sh'aft 32 is slightly flared asseen at 99 and this en d extends into the discharge conduit i3. Substantial clearance is provided between the conduit i9 and the rotatable tubular shaft end 89 for purposes which will be later described.

The inner sleeve 8 is rotatably supported on bearings it carried on the inner sleeve supporting members i2. As previously noted the supports i2 are of opposite hand at the opposite ends of the machine but they are otherwise similar. An elongated generally rectangular slot 99 (Fig. 3l) extends through the wall of the 'sleeve 9 and permits the vane V to have a sliding fit therein. Grooves 9| and 92 are formed at the opposite edges of the slot 99, groove 9| being on the leading edge of the slot and groove 92 being on the Sealing bars 99 are disposed in each of the slots 9i and 92 (see Fig. 35). These bars have bent end portions 99 which are chamfered on their inner surfaces as shown at 95 in Figure 34 so that, when installed in the grooves 9| and 92 they conform to the curvature of the inner surface of the sleeve. The blade engaging edges of the bars 93 are'tapered so that a substantially line contact is formed at 99 between the sealing bars and the concave surfaces 'i9 and 1| of the vane face plates E9 and 66. As the bar 93, which is disposed in the slot 92 on the trailing posed in slot 9| and will urge the bar 93 into contact with the concave surface 1| on the leadingl edge wear plate 66. By tapering or chamfering the inner edge of the bar 93 a passage is provided at the base of the slot 9| which permits the pressure applied through the holes 99 to be transmitted equally over the rear edge surface |99 of the seal bar. As bar99 has a sliding t in the slot 9| an effective sealing contact is maintained at all times between both the leading and trailing bars 93 and their corresponding surfaces on the vane V. Wear of the parts is automatically compensated for and leakage past the vane at the edges of the slot 99 is eectively prevented. The design of the seal bars 93 is such that they may be used interchangeably in either the leading or trailing edge of the slot in the sleeve. Endwise movement of the seal bars is prevented by the hooked end portions 94 which extend around the ends of the slot 99 and are engaged by the ends of the vane V.

It will be observed from Figures 2 and 35 that the edges 91 and 99 of the slot 99 are largely ex- .posed to the pressure which exists outside of the sleeve. The bars 99 are disposed adjacent the inner surface of the sleeve so that an area having substantial width is exposed and acted upon by the pressure adjacent thereto. As edge 99 is disposed in the pressure part of the pump on the leading edge of slot 99, and edge 9i inv the suction part of the trailing edge of slot 99, a pressure differential exists between these -edges which tends to rotate the sleeve 9 in the direction of rotation of vane V. In the same manner outer sleeve 'E is assisted in rotation by the pressure differential between the edges of its vane slot and thus only a portion, of the effort for rotating sleeves l and 9 is imparted from the vane V directly. This mode .of operation greatly reduces wear between the vane and sleeves.

At each end of the sleeve 9, between the ends of the slot 99 and the ends of the sleeve, is a series of inwardly inclined lfluid inlet holes |99. These holes |99 also slant in the direction of rotation of the sleeve as seen in Fig. 1l. The innerdiameter of the sleeve 9 is enlarged at |92 and |99 to provide a running t over the surfaces |99 of the inner sleeve supporting member l2 (see Figs. l and i4). The sleeve ends are again enlarged at |99 and |99 to fit` the outer races of the sleeve supporting bearings i9. In order to provide means for applying iiuid pressureto prevent entry of lubricant from the bearings into the pump chamber inclined holes |91 are drilled through the wall of the sleeve 8 between the holes |9| and the sleeve ends. Four of these `holes mi are shown at each end but itwill be understood that any suitable number might be employed and their function will be more fully described later.

The outer sleeve 'l is not illustrated in detail but is generally similar in its form and arrangement tothe inner sleeve shown in Figures 3l, 32 and 35. As is seen in Figure 2 the outer sleeve 1 is slotted at Ill to permit the vane V to extend therethrough. The edges of the slot IUS are provided with sealing bars |09 which are identical with bars 93 in the inner sleeve 8. Holes I I. extend from the pumpingchamber into the groove which accommodates the bar |09 on the leading edge of the slot in sleeve 1 and the pressure existing adjacent the opening of the holes III) during operation of the machine is effective to maintain sealing engagement between the edges of the slot Il!! and the side faces of the vane V.l Air inlet holes III extend slantingly inwardly through the sleeve 1 (see Figs. l and 11) and are disposed around the entire circumference of the sleeve. A running fit is provided between the surfaces II2 of sleeve 1 and the peripheral portion III of the large sleeve supporting member In (Fig. 13). The ends of the sleeve I n t over the outer races of the bearings 9 and thus it will be seen that rotation of the vane V will cause4 simultaneous rotation of the outer sleeve 'I about its center of rotation b.

To permit air to enter the space within the small sleeve 8 a series of holes III are provided in the wall of the large bearing support Il) (Fig. 1l). The-holes IM are located on the upper half oi' the member I0 while'on the lower half somewhat smaller holes IIS are provided to serve the same purpose..

As will be more fully explained later, fluid may enter or leave the space A within the inner sleeve i through the series of holes IIB in the end housings 3 and .4, then through holes III in the rocent shaped surfaces 23 on the end housings l and 4 and the ends of the inner crescent shaped pumpingchamber C are closed by the generally crescent shaped surfaces 22 of the large bearing supports III (see Fig. 2). As the ends of the vane V also engage the surfaces 22 and V23 it will be observed that rotation of the vane V in the direction indicated by the arrow in Figures 2 to 6 will result in displacement of fluid within the crescent shaped pumping chambers B and C. The term "crescent shaped is not intended to be used in itspurely technical sense in describing the pumping chambers B and C and in the appended claims, but is used asa convenient descriptive term for the cross-sectional shape of these chambers which shape is, strictly speaking, that of the area between internaliy'tangent circles of different diameters.

vStarting with the vanein the position shown in Figures 2 and 6 and rotating in the direction of the arrow, as the vane moves fluid in the chamber B will be forced through the slots 69, chambers SI and holes 53 into the passage 35 within the shaft 32. Such fluid will of course tating outerl sleeve, holes III and IIB in the stationary outer sleeve support I0, and holes IDI in the rotating inner sleeve 8. A free passage for fluid is provided into each end of the inner sleeve 2 during all conditions of operation of the device. If desired, screens IIS'L may be clamped around the end housings 3 and 4 over the inlet holes to prevent the entry of objectionable substances to the supercharger. yAs seen in Fig. 11 at IIB", the screens are spaced from the outside of holes IIG so that the area of these holes will not be obstructed by the screens. Y

When our improved rotary engine is used as a pump the fluid inlet is through the passages I I6, etc., just described and the discharge or outlet is through the aperture in the hollow shaft 32 and the tubular member Il. When the apparatus is used as a fluid pressure motor the operating fluid under pressure is supplied through the conduit I3 and hollow shaft 32 and discharged through the holes described just above in the inner and outer sleeves, the outer sleeve supports and the end housings.

'I'he operation of our mechanism as a fluid pump will now be described, particular reference being had to Figures 2 to 6, inclusive.

Assuming that the apparatus is employed for use as an airplane cabin supercharger, air may at all times freely enter the space A within the small sleeve 8 and outside of the shaft and vane through holes Ils, III, Ill and IM. From this space A, as is clearly seen in Figure 6, communication is maintained at all times to the rear or trailing edge of the vane V through the holes 29, passages and openings 60, A generally crescent shaped outer pumping chamber B is defined by the inner surface of the stationary cylinder I and the outer surface of the rotating sleeve 1 and a second, generally crescent shaped, inner pumping chamber C is defined by the inner surface of the outer sleeve 1 and the outer surface of the inner sleeve l. The ends of the outer pumping chamber B are closed by the crespass out through the outlet in the conduit I 3. 'Ihis pumping action occurs because as the vane rotates uid cannot move from the pressure portion of the chamber B on the leading side of vane V, past the point of tangency T between the outer sleeve and the cylinder I into the suction portion of the chamber B, on the trailing side of vane V. At the same time, keeping in mind that we are referring now to Figure 2, fluid is entering the passages 5I through the inner por-l tion of the slots 89 from the pressure part of the inner chamber C. 'I'his pumping action occurs because of the tangent relation between the inner sleeve 8 and the outer sleeve 1 which prevents the movement of uid past the point of tangency T' between the two sleeves.- The portions of the chambers B and C which lie on the trailing side of the vane V are, as will be seen from Figure 6, both connected to the atmosphere, or other source of fluid to be pumped through the slotted openings 60, ports 55 an 29, inlet chamber A and the previously described communications to the outside of the housing.

AAs the vane V rotates the relative size of the pressure and suction portions of chambers B and C vary and when the vane is moved through into the position shown in Figure 3 fluid is entering the discharge chambers 5I only from the outer pumping chamber B, as it will be observed that the sealing bars 93 which define the slot in the inner sleeve 8 are positioned above the top of the holes 69. In like manner inlet air is entering only the trailing portion of chamber B (on the left hand side of the vane in Fig. 3) and the inlet connection to the chamber C is closed off in the same manner as the discharge connection therefrom. Now, as the vane moves through another 90 into the position shown in Figure 4, communication is again established between both chambers B and C and the discharge passages il and pumping is effected from both chambers simultaneously. At this point in the cycle fluid is also entering both chambers on the trailing side of the blade. The next illustrated position is 'shown in Figure 5 in which the vane has reached its upper vertical position wherein the sealing bars I09 in the outer sleeve 1 have completely shut oir the discharge openings 69 from outer chamber B and the openings B9 extend for substantially their full length into the inner pumping chamber C. At the same time the inlet openings -80 are also disposed entirely lwithin the chamber C and are completely shut o from the outer chamber B.

From the above it will be observed that during rotation of the vane V a 'substantially constant displacement or movement of iluid takes place into the discharge passages in the vane and out through the outlet 35. When maximum pumping is taking place rfrom the outer pumping chamber B the vane is moving through its non-pump ing or zero zone insofar as the chamber C is concerned. When the vane is rotated through 180 it is pumping its maximum value entirely from the inner pumping chamber C and is passing over the non-pumping point of the outer chamber B. At points between these 180 positions of the vane V pumping is effectedboth from outer chamber B and inner chamber C in varying degrees but Wlth'a substantially constant total output for any given increment of rotatiori.

In eect two pumping chambers are combined with a single vane in such a manner that the we provide means for applying the pressure created by the pump on all clearance spaces around the bearings in such a manner that it opposes travel of lubricant toward the pumping chamber. The passages which obtain this result will be described with particular reference to the discharge end of the pump, Ibut it will be understood that similar passages are included on the drive end of the pump and such passages will be referred to by like reference characters when mentioned.

A hole 1 extends through the wall of the tubular shaft member 32 into alignment with a hole ||8 in the driving shaft member 25. A corresponding hole in the opposite end of the driving shaft member is connectedl to the discharge passage by means of the hole 3S and the clearance which isprovided at the bottom of e the bore 28 in the shaft member 25 (see Fig. 1).

Hole ||8 is aligned with an internal groove |20 in the inner sleeve support |2 and thus connection will be established with the groove |20 at any usual drop to zero which is characteristic .of vane type pumps is completely eliminated. Furthermore, our arrangement of inner and outerv sleeves rotatable on different centers within a xed cylinder, the greatest radial width of the outer crescent shaped chamber thus formed being in radial alignment with the minimum radial width of the inner crescent shaped chamber, makes it possible to employ the general arrangement described herein as a luidpressure actuated motor. By applying iluid under pressure through the shaft 32 and out through the chambers 5| and outlets 69 pressure will 'be built up within the chambers B and C which will move the vane in clockwise direction, as seen in Figures 2 to 6. This motion will be continuous because no simultaneous interruption occurs in the supply of iiuid under pressure to the chambers B and C. When the chamber B is not receiving pressurelchamber C is receiving the entire fluid supply and similarly, when chamber B is not receiving pressure chamber C is receiving the entire supply.

If for any reason it is desired to drive the pump illustrated herein in the opposite direction from that shown, it is only necessary to take the pump apart and reassemble the parts with the vane V and sleeves l and 8 reversed end for end. This reversal of the vane Vis made possible by providing the two sets of holes 5t and si in the vane and the corresponding two rows of holes 28 in the shaftf The sleeves l and s are reversed so that the holes 88 and il@ will be located on the' pressure side of the vane during pump operation.

Thus, althoughv we have described our invention as particularly embodied in a fluid pumping apparatus, it will be seen by those skilled in the art that it is also adaptable for use as a uid pressure motor of non-.stalling characteristics which can not stop on a dead center in such a way that it will not start again immediately upon application of pressure.

As noted previously, the illustrated embodiment of our invention is particularly intended for use as a cabin supercharger for aerial vehicles. In such use it is extremely important that no oil, grease or other foreign substances enter the pumping chamber. Preferably the pumping chamber is run dry in order to avoid the possibility of discharging any undesirable material into the cabin with the air supply. In order to prevent any possible entry or lubricant from the bearings 8, it and I8 into the pumping chambers B and C or into the inlet passages of the pump,

point during rotation of .the shaft S. Connecting passages |2| and |22 extend to a groove |23 in the outer circumference of the portion |04 of the member I2. As will be seen in Figure 1, the inner ends of thelholes |01 in the inner sleeve 8 lie on the groove |23 and the holes communicate at their outer ends With a groove |24 in the recess in the outer sleeve support I0. A hole |25 extends from groove |24 to a groove |26 on .the outer surface of sleeve supporting member I0 and the inclined holes |21 in the outer sleeve l have their inner ends arranged in alignment with the groove |26 and their outer ends in alignment with a groove |28 in the end housing 3.

Pressure from the discharge passage 35 is transmitted through the above described series of holes and grooves and is first applied to the groove |20 which is located in the running fit between the enlarged portion 25 'of the shaft and the cup shaped part i9 of the shaft support l2. Thus, the escape of lubricant from bearing |8 into the interior of the inner sleeve 8 is prevented. The -pressure is then carried on to the groove |23 which lies at the running fit between the inner sleeve 8 and the inn'er sleeve support member |25 Pressure in this groove prevents the passage of lubricant from the bearing i5 through the running t clearance into 'the inlet passages of the pump. From groove |23 pressure is applied through holes mi in sleeve 8 to groove |2fi and from groove |25 to groove v|26 through hole |25. From groove |2t`pressure is transmitted togroove |28 through holes |27 in sleeve The grooves |26 and |28 are located respectively in the running ts between the inner surface of the outer sleeve 'l and the outer sleeve support i8 and between the outer surface of the outer sleeve l and the end housing 3. These two grooves |28 and |28 apply pressure which lprevents movement of lubricant from the bearing 8 into the inlet passages of the pump.. Similar arrangement of grooves and passages on the opposite end of the pump protect the drive end inlet passages from lubricant.

Any air which may pass outwardly through the running fit between the shaft member 25 and ele` ment may pass through the bearing I8 and then through a hole |29 to the bearing i8. After passing through the bearing it such air and any other air which may leak through into the bearing |6 between the inner sleeve l and the member I8 may pass through a hole |38 into the bearings 9. After passing through the bearing 8 such air may escape to atmosphere through a hole |3| bore in theshaft supporting member I2 and a hole |33 extends from this groove to the groove |23 in the outer surface of member I2. By means of the hole |33 pressure which is supplied to the groove |23 is applied to the groove |32 around the shaft 32. 'Ihis pressure acts to prevent the escape of lubricant from the bearing I8 outwardly toward the end of the shaft and thus prevents leakage of lubricant into the air being discharged through outlet conduit 3. Similarly, on the drive end of the shaft the corresponding groove |32 and its pressure connection prevents leakage of lubricant out around the drive end of the shaft.

Reference has previously been made to the clearances between the flared end 89 of the hollow shaft portion 32 and the discharge conduit .portion |3. An annular groove |34 is formed in the shaft supporting member |2 and this is connected to a groove |35 in the large sleeve support ID by a hole |36. The groove |35 is connected by holes |31 and |38 to the air inlet passages of the pump and, when air is being discharged through the flared end 89 of the tubular shaft, a, certain amount of air is drawn into the space between the ared end 89 of the shaft and the conduit yI3. This air is: relatively cool, coming directly from atmosphere, and will be mingled and discharged-with air which has been pumped by the vane V. In some instances it may be desirable to so supply cool air where the air being pumped has been heated materially due to the work imposed upon it. This cool air also cools the adjoining .parts of the discharge end of the extends, said second named sleeve being supported eccentrically of said cylinder with-its longitudinal center line on the opposite side of the longitudinal center line of said shaft from that of said rst named sleeve, a constantly open passage permitting the flow of fluid at all times between opposite sides of said vane within said second named sleeve, said vane having constantly open inlet apertures on one side thereof and constantly open discharge apertures on the other side thereof communicating with the space between said sleeves and the space between said outer sleeve and saidcylinder, said inlet apertures being connected to the space within the secondnamed sleeve, and said shaft having a hollow portion connected to said discharge apertures.

2. Apparatus of the type described, including a cylinder, a sleeve supported for rotation Within said cylinder and eccentrically of said cylinder, a second sleeve rotatably supported Within said first named sleeve and eccentrically of said cylinder on the opposite side of the longitudinal axis of said cylinder from said first named sleeve, each of said sleeves being slotted, a vane extending through said slots in said sleeves and being supported for rotation concentrically with said cylinder, a constantly open passage permitting the flow of fluid at all times between opposite sides of said'vane within said second named sleeve, constantly open means communicating with the space within said second-named sleeve for conducting fluid to the interior of saidcynder on one side of said vane, and constantly open'means for conducting fluid from the other side of said vane to a point removed from said cylinder, both said conducting means communicating with the space between said sleeves and the space between said outer sleeve and said, cylinder..

3. In apparatus of the type described, a fixed 40 cylinder, a shaft within said cylinder and coaxial pump. Furthermore, it is possible to increase the 'overall deliveryv of air from the unit by this means but it will also be understood that in many cases this auxiliary air supply may be completely omitted.

Additional effective cooling of the pump bearings, etc., is provided by our dual arrangement of the inlet passages whereby cool air is drawn into each end ofv the pump housing, thus protecting the running parts at both ends of the mechanism.

from heat generated by operation of the pump.

Although we have described the illustrated embodiment of our invention in considerable detail, it will be understood that numerous variations may be made in the form and arrangement of the parts. We do not, therefore, wish to be limited to the particular arrangement and uses of our invention herein described but claim as our invention all the embodiments thereof coming within the scope of the appended claims.

We claim:

I l. In pumping apparatus, a stationary cylinder, a rotatable shaft concentric with and extending through said cylinder, a vane carried by said shaft and adapted to t closely within said cylinder. a cylindrical sleeve disposed around said shaft and having a slot through which said vane extends, means for supporting said sleeve for free rotation within said cylinder, the longitudinal center line of said sleeve being disposed on one side of the longitudinal center line of said shaft.

a second sleeve disposed within said first named sleeve and having a slot through which said vane therewith, a cylindrical sleeve of smaller diameter than said cylinder supported for rotation within said cylinder about an axis spaced from the axis of said cylinder, said sleeve substantially engaging said cylinder, a second cylindrical sleeve of smaller diameter than sai-d iirst named sleeve and supported within said rst named sleeve for rotation about an axis spaced from said axis of said cylinder and on the opposite side thereof from the axis of said first named sleeve, said smaller sleeve substantially engaging said rst named sleeve and being spaced from said shaft through the -peripheral extent thereof, Said sleeves each having a longitudinally extending slot, a vane extending from the central portion of said cylinder to the inner wall thereof and supported for rotation about said axis of said cylinder and extending through said slots in said sleeves and having sliding engagement therewith. a constantly open passage permitting the flow of fluid at all times between opposite sides of said vane within said smaller sleeve, end closure members for said cylinder, 'said vane having its outer edge. slidably engaging the cylinder wall and its ends slidably engaging said end closures. constantly open uid inlet means for the space between said smaller sleeve and said shaft, constantly open means for permitting fluid to flow from said last-mentioned space into the spaces within said cylinder between said sleeves and between said outer sleeve and said cylinder on one side of said vane, and-constantly open means for conducting fluid from said last-mentioned spaces from the opposite side of said vane.

4. In a fluid pump or motor of the type described having a cylinder, a vane supported for coaxial rotation relative to said cylinder, shaft means for supporting said vane. cylindrical sleeves of different diameters disposed within said cylinder, said sleeves being individually sup-.- ported for rotation 'about axes disposed on opposite sides of the axis of rotation of said vane, there being clearance between the inner of said sleeves and said shaft means throughout the peripheral extent of the shaft, and said vane projecting through said sleeves whereby rotation of said vane rotates said sleeves, said sleeves being dimensioned so that each successive increment of rotation of said vane will displace a substanf tially equal volume of the spaces between said sleeves and between `said cylinder and the outer of said sleeves.

` 5. In a fluid pump, a cylinder, an outer sleeve supported for rotation in saidl cylinder and of smaller diameter than said cylinder, said -sleeve engaging the inner Wall of said cylinder to form a crescent shaped outer pumping chamber. an inner sleeve of smaller diameter than said outer sleeve, said inner sleeve being rotatably supported within and in engagement with said outer sleeve to form a crescent shaped inner pumping chamber, said inner pumping chamber having its greatest radial dimension in radial alignment -with the minimum radial dimension of said outer pumping chamber, the greatest radial dimension of said inner pumping chamber being larger than the greatest radial dimension of said outer pumping chamber, said crescent shaped chambers having' substantially equal volume. said sleeves each having a slotted aperture. a vane supported for rotation about the longitudinal axis of said cylinder and extending through said slotted apertures in said sleeves, both sides of said vane being constantly in communication with the entire space within the inner sleeve inlet means for conducting fluid to said pumping chambers on one side of said vane, and discharge means for conducting iluid from said pumping chambers on the opposite side of said vane.

6. In a fluid pump, a stationary cylinder, an outer sleeve supported for rotation in said cylinder and of smaller diameter than said cylinder, said sleeve engaging the inner Wall of said cylinder to form a crescent shaped outer pumping i longitudinal axis of said outer sleeve being disposed on the opposite side of the longitudinal axisl of said cylinder from the longitudinal axis of said inner sleeve said sleeves each having a slotted aperture, a vane supported for rotation about tbe longitudinal axis of said cylinder and extending through said slotted apertures in said sleeves. means for conducting incoming iiuid to said pumping chambers on one side of said vane, and means for conducting outgoing fluid from said pumping chambers on the opposite side o'f said vane. said last named means including a conduit extending from outside of said cylinder and terminating in an aperture in the leading edge of said vane.

7. In apparatus of the type described, a stationary cylinder, an outer cylindrical sleeve supported for rotation in said cylinder and of smaller diameter than said cylinder, said sleeve engaging the inner wall of said cylinder to form an outer chamber of crescent-shaped cross-section, an inner cylindrical sleeve of smaller diameter than said outer sleeve, said inner sleeve being rotatably supported within and in engagement with said outer sleeve to form an inner chamber of crescent-shaped cross-section, said chambers being of substantially equal volume said inner chamber having its greatest radial dimension in radial alignment with the minimum radial dimension of said outer chamber and the longitudinal axis of said outer sleeve being disposed on the opposite side of the longitudinal axis of` said cylinder from the longitudinal axis of said inner sleeve, said sleeves each having aslotted aperture, a vane supported for rotation about the longitudinal axis of said cylinder and extending through said slotted apertures in said sleeves,

means for conducting uid through said vane to said chambers on one side of said vane, and means for conducting fluid through said vane from said chambers on the opposite side of said vane.

8. In a duid pump. a stationary cylinder, an outer cylindrical sleeve rotatably supported in said cylinder and of smaller diameter thanv said cylinder, said sleeve engaging the inner wall of said cylinder to form a. crescent shaped outer pumping chamber, an inner cylindrical sleeve of smaller diameter than said outer sleeve, said inner sleeve being rotatably supported within and in engagement withsaid outer sleeve to form a crescent shaped inner pumping chamber, said inner and outer pumpingchambers being of substantially equal volume, said inner pumping chamber having its greatest radial dimension in radial alignment with the minimum radial dimansion of said outer pumping chamber and the longitudinal axis of said outer sleeve being disposed on the opposite s ide of the longitudinal axis of said cylinder from the longitudinal axis of said inner sleeve, said sleeves each having a slotted aperture, a vane supported for rotation about the longitudinal axis of said cylinder and extending through said slotted apertures in said sleeves, inlet means for conducting uid through said vane to said pumping chambers on one side of said vane, and discharge means for conducting fluid through said vane from said pumping chambers on the opposite side of said vane, said inlet means including a passage extending from said one side of said vane into said inner sleeve and a passage extending from within said inner sleeve to the outside of the pump. and said discharge means including a hollow shaft secured to said vane anda passage extending from said opposite side of said vane into said hollow shaft, said hollow shaft being adapted to discharge fluid outside of said pumping chambers, there being clearance b'etween said shaft and the inner sleeve throughout the peripheral extent ofthe shaft.

9. In a uid pump, `a stationary cylinder, an outer cylindrical sleeve rotatably supported in said cylinder and of smaller diameter than said cylinder. said sleeve engaging the inner wall of said cylinder to form a crescent shaped outer Dumping chamber, an inner cylindrical sleeve of smaller diameter than said outer sleeve. said inner sleeve being rotatably supported within and in engagement with said outer sleeve to form a crescent shaped inner pumping' chamber, said inner pumping chamber having its greatest radial dimension in radial alignment with the minimum ber and the longitudinal axis of said outer sleeve being disposed on the opposite side of the longitudinal axis of said cylinder from the longitudinal axis of said inner sleeve, said sleeves each having a slotted aperture, a vane supported by a hcllowshaft for rotation about the longitudinal axis of said cylinder and extending through said slotted apertures in said sleeves, inlet means for conducting fluid through said vane to said pumping chambers on one side of said vane, and discharge means for conducting uid through said vane from said pumping chambers on the opposite side of said vane. said inlet means including a passage extending from an opening in said one side of said vane into said inner sleeve and a passage extending from within said inner sleeve and on the exterior of said shaft to the outside of the pump. and said outlet means including said hollow shaft secured to said vane and a passage extending irom an opening in said opposite side of said vane into said hollow shaft, said hollow shaft being adapted to discharge fluid outside of said pumping chambers, said openings in the sides of said vane extending radially into both said outer and inner pumping chambers during part of the rotation of said vane and into only one of said chambers during the other parts of the vane rota tion.

.10. Apparatus of the type described comprising a cylinder. a vane rotatable in said cylinder. means supporting said vane for rotation. two non-concentric cylindrical sleeves rotatably supported one within the other in said cylinder. said sleeves' being of such diameter that they form Ainner and outer crescent-shaped chambers having substantially equal volume. said vaneextending through said sleeves. means for conducting` fluid to said chambers on one side of said vane. and means for conducting fluid from said chambers on the opposite side of said vane.

l1. In apparatus of the type described. a cylinder, a cylindrical outer sleeve of smaller diameter than said cylinder and supported forA rotation therein and substantially tangent thereto, an inner sleeve supported for rotation in said outer sleeve and tangent thereto, the longitudinal axis of said outer sleeve being disposed on the opposite side of the longitudinal axis of said cylinder from the longitudinal axis oi saidiinner sleeve, said sleeves being. slotted. a vane supported by a tubular member for rotation in said cylinder and extending through said slots. means for maintaining fluid conducting passages extending from outside of said cylinder -to the intioned passage.

12. In a pump of the type described, a housing having a cylinder portion, slotted inner and outer f sleeves disposed eccentrically in said cylinder, the axes of said sleeves being disposed on opposite sides of the axis of said cylinder portion, fluid inlet and outlet means for the space between said outer sleeve and said cylinder and for the space between said sleeves, bearings for said sleeves in said housing, a vane extending through said slots in said sleeves, a shaft for saidvane, bearings for said shaft, the operation of said pump ascuas y creating pressure within said cylinder on one side of said vane, and means for applying pressure so generated against said sleeve and shaft bearings in a direction to resist leakage of lubricant therefrom into said cylinder.

13. In a pump of the type described, a housing having a cylinder portion, slotted inner and outer sleeves disposed eccentrically in said cylinder, the axes of said sleeves being disposed on opposite edges of the axis of said cylinder portion, nu-

id inlet and outlet means for the space between said cuter sleeve and said cylinder and for the space between said sleeves, bearings for said sleeves in said housing, a vane extending through said slots in said sleeves, a shaft for said vane.

bearings for said shaft, the operation of said pump creating pressure within said cylinder on one side oi' said vane means for applying said pressure against said sleeve and shaft bearings in o aIdirection to resist leakage of lubricant therein said sleeves, a shaft for said vane having a tubular central fluid conduit portion and a wall A portion, said wall portion being slotted to permit insertion of said vane, said vane having an opening on one side thereof and another opening on the other side thereof, fluid passages from one of 5 said openings into said tubular conduit. and fluid passages from the other of said openings through said shaft wail portion into the space within said inner sleeve, said fluid passages being positioned to permit end to end reversal of said vanein said o slot in the wall portion of said shaft while maintaining said fluid connections whereby reverse rotation of the apparatus may be had.

l5. In apparatus of the type described. a cylinder, a vane supported coaxially with said cylin- 5 der for relative rotational movement thereto, an outer cylindrical sleeve supported within said cylinder for rotation relative thereto on an axis parallel to and on one side oi' the common axis of said cylinder and vane, an inner cylindrical sleeve o supported within said outer cylindrical sleeve for rotation relative to said cylinder on an axis parallel to but on the opposite side of the common axis of said cylinder an'd vane from the axis of said outer sleeve. said vane projecting through said sleeves for sliding movement relative thereto, constantly open means for conducting fluid to the spaces between said cylinder and the outer of said sleeves and between said sleeves. on one i side of said vane, and constantly open means for conducting fluid from said spaces on the opposite side of said vane to a point removed from said cylinder, said spaces being of substantially equal volume.

16. In apparatus of the type described, a cylo5 inder, a shaft rotatable relative to said cylinder and supported concentrically therewith. a vane supported by s aid shaft and adapted to .have a running fit within said cylinder, a cylindrical sleevedisposed around said shaft and having a slot through which said vane extends, the longitudinal axis of said sleeve being disposed on one side of the longitudinal axis of said shaft and cylinder, a second sleeve disposed within said first named sleeve and having a slot through which said vane extends, said second named sleeve being supported eccentrically of said cylinder with essere@ gg its longitudinal axis disposed on. the opposite side of the longitudinal axis of said shaft and cylinder from the longitudinal axis of said first named sleeve a distance whereby each successive increment of rotation of said vane will` displace a sub'- stantially equal volume of the spaces between said sleeves and between said' cylinder and the outer sleeve, said vane having an inlet aperture on one side thereof and a discharge aperture on the other side thereof, said apertures communicating with said. spaces and said shaft having a hollow portion connecting to one of said aper- 5. tures.

JOSEPH F. JAWOROVSH. NORBERT JAWOROWSM. 

